A cleaning machine exhaust assembly and a cleaning machine

Abstract

The utility model discloses a kind of washing machine exhaust components and washing machine, the washing machine exhaust component includes: shell;Exhaust passage, it is formed in shell, the exhaust passage has the first port for gas and noise to enter and the second port for gas and noise to discharge;The exhaust component further includes at least two sound-absorbing structures, the sound-absorbing structure is arranged in the wall surface outside of exhaust passage, the connection of the wall surface of exhaust passage and sound-absorbing structure is provided with perforation and can be for sound wave to enter sound-absorbing structure, the length of at least two sound-absorbing structures and / or the radius of connection place with exhaust passage is not identical.

Description

Technical Field

[0001] This utility model relates to household appliances, and in particular to a cleaning machine exhaust assembly, and a cleaning machine using the exhaust assembly. Background Technology

[0002] As living standards improve, consumers have increasingly higher requirements for the noise levels of household appliances. For example, the cleaning noise of washing machines has become increasingly lower, resulting in more prominent drying noise.

[0003] Exhausting is a crucial part of the drying process. Existing exhaust methods can be found in Chinese patents such as those filed by the applicant (application numbers 202210770108.3 and 202210721397.8). These methods involve using a fan to draw water vapor from the dishwasher cavity into the exhaust channel and then expelling it to the outside of the machine.

[0004] The long exhaust operation time, especially with increasing user demands for drying efficiency, has led manufacturers to increase fan power, making noise a significant issue. Existing noise reduction solutions in exhaust ducts typically involve attaching porous sound-absorbing materials such as sound-absorbing cotton to the inner walls of the duct or at the air inlet to absorb sound transmitted from the fan and the duct.

[0005] The noise reduction range of sound-absorbing cotton is small. Moreover, since the function of the exhaust channel is to remove water vapor from the cleaning machine cavity, it is in a high-temperature and humid environment. When using porous sound-absorbing materials for noise reduction, it will absorb condensation water, resulting in a decrease in performance. Furthermore, the sound-absorbing cotton will grow mold in a long-term humid environment, affecting the hygiene of the cleaning machine. Utility Model Content

[0006] The first technical problem to be solved by this utility model is to address the shortcomings of the existing technology by providing a cleaning machine exhaust assembly that expands the noise reduction frequency range and improves the noise reduction effect.

[0007] The second technical problem to be solved by this utility model is to provide a cleaning machine that uses the above-mentioned exhaust components.

[0008] The technical solution adopted by this utility model to solve the first technical problem mentioned above is: a cleaning machine exhaust assembly, comprising:

[0009] shell;

[0010] An exhaust passage formed within the housing, the exhaust passage having a first port for gas and noise to enter and a second port for gas and noise to exit;

[0011] Its features are:

[0012] The exhaust assembly further includes at least two sound-absorbing structures, which are disposed on the outer side of the wall of the exhaust channel. The connection between the wall of the exhaust channel and the sound-absorbing structure is provided with perforations to allow sound waves to enter the sound-absorbing structure. The lengths and / or radii of the connection between the at least two sound-absorbing structures and the exhaust channel are not the same.

[0013] Since the sound transmitted from the exhaust channel is a broadband noise, and a single resonant cavity can only absorb noise of a single frequency, the sound-absorbing structure is equivalent to the neck of the resonant cavity. By adjusting the length and cross-sectional area of ​​the neck, different sound-absorbing structures can absorb noise of different frequencies. As a result, multiple resonant frequencies are generated at different sound-absorbing structures, achieving multi-frequency noise reduction and realizing a noise reduction structure with broadband sound absorption.

[0014] Furthermore, to facilitate defining the exhaust channel, the length direction of the exhaust channel is the Z-axis direction, the width direction of the exhaust channel is the X-axis direction, the depth direction of the exhaust channel is the Y-axis direction, the X-axis, Y-axis and Z-axis directions are mutually perpendicular, and the first port and the second port are arranged at intervals along the Z-axis direction.

[0015] The outer casing contains two plates spaced apart along the X-axis, which together with the outer casing form the exhaust channel.

[0016] Preferably, in order to enable the noise sound waves to be reflected multiple times and improve the noise reduction effect, the exhaust channel is configured as a sound flow type silencer channel. The inner surface of each plate constituting the exhaust channel includes one or at least two curved surfaces or planes connected end to end. On the cross section of the plane formed by the X-axis and Z-axis, the inner surface is wavy or sawtooth.

[0017] Preferably, in order to allow the noise sound waves to be reflected multiple times and improve the noise reduction effect, the length direction of the exhaust channel is the Z-axis direction, the width direction of the exhaust channel is the X-axis direction, the depth direction of the exhaust channel is the Y-axis direction, the X-axis, Y-axis and Z-axis directions are perpendicular to each other, and the first port and the second port are arranged at intervals along the Z-axis direction.

[0018] The exhaust channel has an overall S-shaped cross-section on the plane formed by the X-axis and Z-axis.

[0019] Preferably, to facilitate the entry of sound waves into the sound-absorbing structure, the perforation is provided on the wall surface of the exhaust channel along the X-axis direction.

[0020] Furthermore, in order to balance sound absorption and air intake efficiency, the width of the end of the outer shell near the second port, projected onto the plane formed by the X-axis and Y-axis, is L along the X-axis direction. The maximum distance between one side wall of the exhaust channel and the wall of its adjacent outer shell along the X-axis direction is L1, and the maximum distance between the other side wall of the exhaust channel and the wall of its adjacent outer shell along the X-axis direction is L2, and satisfies: 0.8≤(L1+L2) / L≤1.2.

[0021] Preferably, to reduce the impact on airflow velocity, the connection between the sound-absorbing structure and the exhaust channel is transitioned by a rounded corner structure.

[0022] Furthermore, a fan is installed inside the housing, the effective width of the exhaust channel is H, and the width of the fan outlet is h, satisfying H≥h, thereby ensuring good exhaust efficiency.

[0023] The technical solution adopted by this utility model to solve the second technical problem mentioned above is: a cleaning machine, characterized in that: it uses the cleaning machine exhaust assembly as described above.

[0024] Compared with the prior art, the advantages of this utility model are as follows: Since the sound transmitted from the exhaust channel is a broadband noise, and a single resonant cavity can only absorb noise of a single frequency, the sound-absorbing structure is equivalent to the neck of the resonant cavity. By adjusting the length and cross-sectional area of ​​the neck, different sound-absorbing structures can absorb noise of different frequencies. Thus, multiple resonant frequencies are generated at different sound-absorbing structures, achieving multi-frequency noise reduction and realizing a noise reduction structure with broadband sound absorption. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the exhaust assembly of the cleaning machine according to an embodiment of the present utility model;

[0026] Figure 2 This is a cross-sectional view of the exhaust assembly of the cleaning machine according to an embodiment of the present utility model;

[0027] Figure 3 for Figure 2 A magnified schematic diagram of part I. Detailed Implementation

[0028] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments.

[0029] In the description of this utility model, it should be understood that the terms "center," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description. They do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Since the embodiments disclosed in this utility model can be arranged in different directions, these terms indicating direction are only for illustration and should not be regarded as limitations. For example, "upper" and "lower" are not necessarily limited to directions opposite to or consistent with the direction of gravity. In addition, features defined with "first" and "second" may explicitly or implicitly include one or more of such features.

[0030] See Figures 1-3 A cleaning machine exhaust assembly includes a housing 1 and an exhaust channel 2 formed within the housing 1. The housing 1 may have two parts that are snap-fitted together. Figure 1 and Figure 2 The image shows only half of the outer shell 1.

[0031] Furthermore, the outer casing 1 is provided with an air inlet 11, and a fan is installed inside the outer casing 1 (only the mounting cavity 12 for mounting the fan is shown in the figure, the fan itself is not shown). This allows water vapor and other gases to be drawn from the inner cavity of the cleaning machine (such as a dishwasher, fruit and vegetable cleaner, or a cleaning machine that can wash both dishes and fruits and vegetables; see the applicant's prior patents or patent applications regarding cleaning machines) to assist in drying the inner cavity. The outer casing 1 is also provided with an air outlet (not shown) for discharging the gas drawn from the inner cavity to the outside of the cleaning machine. The above structure is prior art and will not be described in detail here.

[0032] The exhaust channel 2 is in fluid communication with the air outlet of the fan. In the installed state, the exhaust channel 2 is typically located below the air outlet of the fan. The exhaust channel 2 includes a first port 21 and a second port 22, where the first port 21 is used for the entry of gas and fan noise, and the second port 22 is used for the exhaust of gas and fan noise. The exhaust channel 2 can be constructed by two plates 23 arranged opposite each other inside the housing 1, cooperating with the housing 1. In this embodiment, the first port 21 is located at the top of the exhaust channel 2, while the second port 22 is located at the bottom of the exhaust channel 2. The direction in which the exhaust channel 2 extends between the first port 21 and the second port 22 is the length direction (Z-axis direction) of the exhaust channel 2. The first port 21 and the second port 22 are arranged at intervals along the Z-axis direction. Here, "interval arrangement" does not strictly require that the first port 21 and the second port 22 be aligned in the X-axis direction (described below); they can be aligned or staggered. The direction in which the exhaust channel 2 extends between the two plates is the width direction of the exhaust channel 2. Figure 2 The X-axis direction is shown in the figure. Each plate is positioned along the depth of exhaust channel 2. Figure 2 The direction perpendicular to the paper plane (i.e., the Y-axis direction) shown in the diagram all extends to contact the outer casing 1 to form a relatively enclosed exhaust channel 2.

[0033] In this embodiment, the exhaust channel 2 is configured as a sound-flow type silencing channel. Each plate forming the inner surface of the exhaust channel 2 includes one or at least two curved or flat surfaces connected end-to-end. On the cross-section of the plane along the length and width directions of the exhaust channel 2 (i.e., the plane formed by the X-axis and Z-axis), the inner surface is wavy or sawtooth-shaped, and the curvature of adjacent curved surfaces can be the same or different. The number of curved or flat surfaces can also be selected as needed. This forms a non-linear air duct, which is beneficial for noise reduction. In this embodiment, the overall shape is S-shaped.

[0034] The exhaust channel 2 has perforations 24 on its wall along its width. A sound-absorbing structure 3 is provided on the outside of the exhaust channel 2. The perforations 24 may be circular, and the sound-absorbing structure 3 may be cylindrical. The sound-absorbing structure 3 is connected to or integrated with the exhaust channel 2. There are at least two sound-absorbing structures 3, which may be distributed on one or both sides of the exhaust channel 2 along its width. The end of the sound-absorbing structure 3 opposite to the perforations 24 is an open end, and the end of the sound-absorbing structure 3 away from the perforations 24 is a closed end. Thus, the exhaust channel 2 and the sound-absorbing structure 3 together constitute a Helmholtz resonant cavity.

[0035] Since a single Helmholtz resonator can only absorb single-frequency sound, but the sound of the exhaust fan and the fluid passing through exhaust channel 2 is relatively wide-frequency sound, in this embodiment, a single resonator is used in combination with necks of different lengths and radii to achieve the function of absorbing wide-frequency noise. The structure is simple, easier to process, and easier to manufacture.

[0036] The formula for calculating the resonant frequency of Helmholtz resonance sound absorption is shown in Formula 1:

[0037]

[0038] Where c is the speed of sound, measured in meters per second (m / s), approximately 343 m / s in air; A is the cross-sectional area of ​​the pipe, measured in square meters (m²). 2 V is the volume of the cavity, measured in cubic meters (m³). 3 ); l is the length of the pipe, in meters (m).

[0039] The noise reduction of the Helmholtz resonator is calculated as shown in formula (2):

[0040]

[0041] Where ΔL is the noise reduction amount, measured in decibels (dB); f is the frequency of the sound wave, measured in hertz (Hz); and f0 is the resonant frequency of the Helmholtz resonator, measured in hertz (Hz).

[0042] Formula 1 shows that the resonant frequency of the Helmholtz resonator is determined by the volume V of the resonator cavity, the cross-sectional area A of the neck, and the length L of the neck. Since a single Helmholtz sound-absorbing structure can only absorb single-frequency noise, while the sound transmitted through exhaust channel 2 is broadband noise, a noise reduction effect on multiple frequency bands is required to achieve a better sound absorption effect.

[0043] Specifically, in this embodiment, the sound-absorbing structure 3 is equivalent to the neck of the resonant cavity, and at least two sound-absorbing structures 3 have different neck radii and / or neck lengths d. i (Axial dimension), the neck radius is equal to the radius r of the perforation 24. This is achieved by adjusting the neck length d. i The cross-sectional area A of the perforation 24 allows different sound-absorbing structures 3 to absorb noise of different frequencies, where A can be adjusted by changing the radius of the neck, and d i This can be achieved by inserting an internal tube. This results in multiple resonant frequencies at three different sound-absorbing structures, achieving multi-frequency noise reduction and creating a sound-absorbing structure with broadband sound absorption.

[0044] To reduce the impact on airflow velocity, a rounded corner structure 31 is used to transition at the connection between the sound-absorbing structure 3 and the corresponding plate 23.

[0045] As mentioned above, the cross-section of the exhaust channel 2 on the plane formed by the X-axis and Z-axis is S-shaped, which allows the sound to be reflected a sufficient number of times within the channel. The more times the sound is reflected within the channel, the better the sound absorption effect.

[0046] The effective width of any position in the exhaust channel 2 (the width dimension that can effectively participate in airflow and make an actual contribution to ventilation volume in the cross-section of the channel, which can be equivalent to the diameter of the inscribed circle at the current position when measured) is H, and the width of the fan outlet is h (shown in the figure is the size of the mounting cavity 12 of the housing 1, which is adapted to the fan), and H≥h is satisfied, thereby achieving better exhaust performance. As mentioned above, in order to improve sound absorption efficiency, the sound needs to be reflected a sufficient number of times in the channel. This will also increase the resistance to airflow. Therefore, in order to balance sound absorption effect and air intake efficiency, the following dimensions are limited: 0.8≤(L1+L2) / L≤1.2. The meanings of each parameter are as follows: the projection on the plane formed by the X-axis and Y-axis, along the X-axis direction, the width of the end of the outer shell 1 near the second port 22 is L, the maximum distance between one side wall of the exhaust channel 2 and the wall of its adjacent outer shell 1 along the X-axis direction is L1, and the maximum distance between the other side wall of the exhaust channel 2 and the wall of its adjacent outer shell 1 along the X-axis direction is L2.

[0047] Therefore, by balancing sound absorption and airflow, the problem of the contradiction between sound absorption and flow resistance was solved, and effective noise reduction was achieved without affecting the exhaust performance.

[0048] The fan speed of the aforementioned cleaning machine can be intelligently voice controlled. To this end, the cleaning machine can be equipped with an intelligent voice control module, which includes a controller, a voice receiving module, and a voice parsing module. The voice receiving module can receive user commands, and the voice parsing module can parse the commands. Based on the parsed commands, the machine can be controlled to perform corresponding operations, thereby realizing intelligent control of the cleaning machine and improving the user experience of this utility model cleaning machine.

[0049] The term "fluid connectivity" as used in this utility model refers to the spatial relationship between two components or parts (hereinafter referred to as the first part and the second part, respectively), that is, a fluid (gas, liquid, or a mixture of both) can flow from the first part along a flow path and / or be transported to the second part. This can be a direct connection between the first part and the second part, or an indirect connection between the first part and the second part through at least one third party. The third party can be a fluid channel such as a pipe, channel, conduit, guide, hole, or groove, or a chamber or combination thereof that allows fluid to flow through.

Claims

1. A cleaning machine exhaust assembly, comprising: Outer shell (1); An exhaust passage (2) is formed inside the housing (1), the exhaust passage (2) having a first port (21) for gas and noise to enter and a second port (22) for gas and noise to exit; Its features are: The exhaust assembly also includes at least two sound-absorbing structures (3), which are disposed on the outside of the wall of the exhaust channel (2). The connection between the wall of the exhaust channel (2) and the sound-absorbing structure (3) is provided with a perforation (24) to allow sound waves to enter the sound-absorbing structure (3). The lengths and / or radii of the connection between the at least two sound-absorbing structures (3) and the exhaust channel (2) are not the same.

2. The exhaust assembly for the cleaning machine according to claim 1, characterized in that: The length direction of the exhaust channel (2) is the Z-axis direction, the width direction of the exhaust channel (2) is the X-axis direction, the depth direction of the exhaust channel (2) is the Y-axis direction, the X-axis, Y-axis and Z-axis directions are perpendicular to each other, and the first port (21) and the second port (22) are arranged at intervals along the Z-axis direction; The outer casing (1) is provided with two plates (23) arranged at intervals along the X-axis direction. The plates (23) cooperate with the outer casing (1) to form the exhaust channel (2).

3. The exhaust assembly for the cleaning machine according to claim 2, characterized in that: The exhaust channel (2) is configured as a sound flow type silencer channel. The inner surface of each plate constituting the exhaust channel (2) includes one or at least two curved or flat surfaces connected end to end. On the cross section of the plane formed by the X-axis and Z-axis, the inner surface is wavy or sawtooth.

4. The exhaust assembly for the cleaning machine according to claim 1, characterized in that: The length direction of the exhaust channel (2) is the Z-axis direction, the width direction of the exhaust channel (2) is the X-axis direction, the depth direction of the exhaust channel (2) is the Y-axis direction, the X-axis, Y-axis and Z-axis directions are perpendicular to each other, and the first port (21) and the second port (22) are arranged at intervals along the Z-axis direction; The exhaust channel (2) has an overall S-shaped cross-section on the plane formed by the X-axis and Z-axis.

5. The exhaust assembly for the cleaning machine according to claim 3 or 4, characterized in that: The perforation (24) is provided on the wall surface of the exhaust channel (2) along the X-axis direction.

6. The exhaust assembly for the cleaning machine according to claim 5, characterized in that: The projection onto the plane formed by the X-axis and Y-axis, along the X-axis direction, the width of the end of the outer shell (1) near the second port (22) is L, the maximum distance between one side wall of the exhaust channel (2) and the wall of its adjacent outer shell (1) along the X-axis direction is L1, the maximum distance between the other side wall of the exhaust channel (2) and the wall of its adjacent outer shell (1) along the X-axis direction is L2, and satisfies: 0.8≤(L1+L2) / L≤1.

2.

7. The exhaust assembly for the cleaning machine according to claim 1, characterized in that: The sound-absorbing structure (3) and the exhaust channel (2) are connected by a rounded corner structure (31).

8. The exhaust assembly for the cleaning machine according to claim 1, characterized in that: A fan is installed inside the outer casing (1), the effective width of the exhaust channel (2) at any position is H, the width of the fan outlet is h, and H≥h is satisfied.

9. A cleaning machine, characterized in that: The application includes the exhaust assembly of the cleaning machine as described in any one of claims 1 to 8.

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